SA517382285B1 - A valve for control of a fluid flow - Google Patents

Abstract

Disclosed is a valve for control of a fluid flow. The valve comprises shaft means (4) comprising a first shaft friction surface (5) and a second shaft friction surface (6) arranged in a mutual shaft friction surface angle (SA). The shaft friction surface angle (SA) is an inside angle between the first shaft friction surface (5) and the second shaft friction surface (6) and the fluid control means (2) is arranged to be displaced along the rotational axis (7) of the shaft means (4) in accordance with a rotation of the shaft means (4). The valve further comprises collar means (8) comprising a first collar friction surface (9) and a second collar friction surface (10) arranged in a mutual collar friction surface angle (CA). The set of collar friction surfaces (9, 10) are arranged to mesh with the set of shaft friction surfaces (5, 6) and wherein the shaft friction surface angle (SA) and the collar friction surface angle (CA) are between 120° and 170°.

Description

A VALVE FOR CONTROL OF A FLUID FLOW Full Description BACKGROUND The invention relates to a valve for controlling the flow of a fluid. The valve includes a gle (valve) and a fluid control device to control the flow of fluid through the (gle) valve; the fluid control device is arranged within the valve housing. The valve also includes a shaft device. The valve that operates it is the shaft - For example, a gate valve - typically comprises a shaft with a grooved segment interlocked with a wedge nut. Such that as the shaft rotates the wedge will be shifted up or down to open or close the fluid path through the valve. To ensure that the shaft is axially fixed it is known for example Example from International Application No. 1a 19518/95 Provide the valve housing with a fixed bushing that meshes with the circular protrusions on the shaft 0. With this design of the valve there is a risk of damage to the wedge” to the shaft or the bushing when the valve is actuated – in particular if the valve is The application of too much torque during the opening or closing of the valve. Thus, from International Order No. (11) 177681/2014 defines the formation of interlocking contact surfaces between the bushing and the shaft at an angle of 45 “Lad is related to the shaft rotation axis to increase the contact surface between the bushing and the shaft and that Friction increases at sab) the Axial force - eg 5 when the wedge reaches its maximum position. Despite this axial mounting method the shaft in relation to the valve housing is not cost effective. The purpose of the invention is therefore to provide a valve comprising a more cost-effective means of fixing the shaft axially with respect to the (soll) of the valve. General description of the invention provides a valve to control the flow of a fluid. The valve comprises a valve and a means of controlling the fluid to control the fluid Fluid flow through the valve (gle) where the control device is arranged in

fluid inside the valve housing. The valve also comprises a shaft device comprising a set of shaft friction surfaces” Cua The shaft friction surface assembly includes a first shaft friction surface and a second shaft friction surface arranged at an angle with a common shaft friction surface. The angle of the shaft friction surface is an internal angle between the friction surface of the first shaft and the friction surface of the second shaft, and the fluid control device is arranged to be displaced along the axis of rotation of the shaft means according to the rotation of the shaft means. The valve additionally comprises a bushing device that includes a set of bushing friction surfaces; The set of bushing friction surfaces includes a first bush friction surface and a second bushing friction surface arranged at the corner of a common bushing friction surface. The angle of the bushing friction surface is an internal angle between the first bushing friction surface and the second bushing friction surface 0 and the bushing friction surface group is arranged to mesh with the shaft friction surface group and where the shaft friction surface angle and the bushing friction surface angle are between 175° 110” (5) Preferably between 170° and 120° it is advantageous to make the shaft and bushing device comprising at least one set of friction surfaces, wherein when the shaft friction set meshes with the set of 5 bushing friction surfaces the fluid control device and shaft device will be; The bushing and/or other parts of the valve are better protected against harmful overloads regardless of the extreme position the fluid control device reaches - for example regardless of whether the gate valve wedge is in the fully open or closed position. A large frictional force will be generated between the shaft device and the bushing device once the axial force is increased - due to the fluid control device reaching the max position 0. The direction of the axial force has no value. On known shafts and bushings - J ie those dual in International Application No. (1) 1 and International Application No. 1 (19518/95) The bushing and shaft should typically have several opposite surfaces to ensure that the friction between the meshing parts is high so that the risk of damage to the different parts of the valve is reduced enough. With this, by forming the friction surfaces of the bushing device and the shaft device at an obtuse angle in the mentioned ranges; It is possible to configure the shaft device and the bushing device with fewer assemblies

of shaft friction surfaces and bushing friction surfaces - such as only one set of shaft friction surfaces and bushing friction surfaces - and still achieve the same degree of friction force. Hereby it is possible to reduce the manufacturing cost of bushing device and shaft device. In addition to this, the obtuse angle between the special friction surfaces is beneficial, as groups of meshing friction surfaces within the mentioned ranges will generate the wedge effect that amplifies the friction/braking effect of the shaft and bushing device for engagement. Thus, the smaller material bushing device will be able to generate the friction effect. Sufficient braking-dull cost and space consumption are reduced. Also additionally if the shaft friction surfaces angle and the shaft friction surface angle

0 The bushing is too small, the wedging effect will be very little, and the surface area must be increased accordingly to achieve the same effect. However, if the friction surface angles are too large, the risk of wedging the joint friction surfaces will become so high that they cannot be easily separated again. thus; Current angle ranges represent a beneficial relationship between effectiveness and functionality.

The term 'fluid control means' is understood in this context

5 that what kind of gateway; skylight; A ball or other type of sigal weir suitable for controlling fluid flow through a

Underground valve.

It should be noted that in this context the term 'shaft means' shall be understood as any type of spindle or other type of shaft suitable for transmitting rotation from the outside of the valve housing to the fluid control device within the housing. led.

Furthermore in this context the term 'collar means' is to be understood as any type of loop; A round flange or other type of bushing is suitable for enclosing the shaft device of a valve and for transmitting axial forces between the shaft device and the valve housing of a valve. However, it should be noted that this does not exclude in any way the possibility of dividing the bushing device axially and/or radially into more than one substantially separated part and/or sector and does not exclude the formation of the bushing device in an integrated form with a shelter

5 valve or other gia of valve.

In one aspect of the invention, the shaft friction surface angle and shaft friction surface angle are significantly reduced

bushing friction. Making the shaft friction surface angle and bushing friction surface angle more uniform is advantageous as we can better match the surfaces - thus the friction between the shaft friction surfaces and the bushing friction surfaces increases when pushed together by axial forces/displacement of the shaft device. In one aspect of the invention, the shaft friction surface angle and the bushing friction surface angle are between 145" and 165©; Mie 154". If the shaft friction surface angle and the bushing friction surface angle are very small, the wedging effect will become very small, and the surface area must be increased accordingly to achieve the same effect. With 0 this is if the friction surface angles are too large the risk of wedging the joint friction surfaces will actually become so high that they cannot be easily separated again. Thus current angle ranges represent a beneficial relationship between functionality and effectiveness. on the side of the invention; The coefficient of friction between the shaft friction surfaces and the bushing friction surfaces is between 0.05 and 2; Preferred between 0.1 and 1 and most preferably between 0.15 and 0.55; Mie 5 0.35. If the friction between the friction surfaces of the shaft and the friction surfaces of the bushing is low, ha, then the interlocking friction surfaces will not generate the desired braking effect and the risk of damage to parts of the valve will increase. However, if the coefficient of friction between adjacent friction surfaces is very high, more force will be required to actuate the valve during normal operation. Thus the current 0 coefficient of friction ranges represent a useful safety and functional relationship. It should be noted that in Glad the term "friction coefficient" is to be understood as a constant coefficient of friction between the dry, non-lubricating friction surfaces of the shaft device and the bushing device. In one aspect of the invention, the ratio between the angles of the friction surface is The coefficient of friction between the 5 shaft friction surfaces and the bushing friction surfaces is between 150 and 1000; preferably between 200 and 800 and most preferably between 300 and 600.

If the ratio between the friction surface angles and the friction coefficient between the friction surfaces is too low, the interlocking friction surfaces will not generate the desired braking effect and the risk of damage to parts of the valve increases. However, if the ratio becomes too high, more force is required to operate the valve during normal operation and/or there is a risk of wetting of the friction surfaces to the point where they cannot be easily separated. Thus the current friction coefficient ranges represent a distinct relationship of safety and functionality.

on the side of the invention; JL substantially a first travel angle between the rotational axle of the shaft device and the first shaft friction surface with a second travel angle between the rotational axle of the shaft device

The drive shaft and the friction surface of the second drive shaft. Formation of the first and second transition angles in a highly symmetrical manner is advantageous

0 Protection against harmful overloads is largely the same regardless of the extreme position reached by the fluid control. In addition, a more uniform design reduces manufacturing and assembly costs.

In one aspect of the invention, the first transition angle and the second transition angle are between 1°C405, preferably between 94 and 30, and the most preferable between 8" 2035©, for example 13".

If the transition angles are too large the wedge effect will be very small and the surface area adjacent to the friction surfaces must be increased accordingly to achieve the same effect. However, if the transition angles are too few, the risk of wedging the joint friction surfaces will become so high that they cannot be easily separated again. Thus current angle ranges represent a beneficial relationship between functionality and functionality.

In part of the invention, the shaft device comprises more than one set of shaft friction surfaces.

Configuring the shaft device with more than one set of shaft friction surfaces is advantageous as the shaft friction surfaces can be distributed over a larger area of the shaft device thus reducing the risk of local stress concentrations.

on the side of the invention; A bushing device has more than one set of surfaces

bushing friction.

Configuring the bushing device with more than one set of bushing friction surfaces is advantageous in that the bushing friction surfaces can be distributed over a larger area of the shaft device and valve housing thus reducing the risk of local stress concentrations. In one aspect of the invention, the shaft friction surfaces assembly is made from a first material and the bushing friction surfaces assembly is made from a second material; And where the first article differs from the second article. If the shaft friction surfaces and the bushing friction surfaces are made of the same material, the risk of wear is greatly increased. Thus it is useful to form the abutting friction surfaces from a material in one aspect of the invention » The set of shaft friction surfaces shall be made of stainless steel. In the valve, the shaft device will extend axially outside the valve housing to enable the fluid control device to be operated from outside the valve housing. However, since the valve may often be buried underground or otherwise placed in a harsh environment, it is advantageous to forge the shaft device from a robust and inert material, such as stainless steel. on the side of the invention; The set of bushing friction surfaces are made of brass. Brass is bale hard and relatively strong which makes it suitable for forming a range of friction surfaces of the bushing. In one aspect of the invention, the shaft friction surfaces group is formed circumferentially on the outer pall of the shaft device, and in one aspect of the invention; The bushing friction surfaces are formed on the inside of the bushing device enabling the shaft friction surfaces and the bushing friction surfaces 0 to interlock easily. In part of the invention » the bushing device comprises at least one complete solid ring. The formation of the bushing device as a continuous link is advantageous as it facilitates the manufacturing process and reduces the logistic problems. In an aspect of the invention » the bushing device is mounted on the shaft device by means of 5 contraction. If the friction surfaces of the shaft and the friction surfaces of the bushing need to be interlocked, the bushing medium is formed

as a continuum; It is advantageous to fit the bushing device to the shaft device by shrinkage as we ensure good contact of the friction surfaces with each other after installation. on the side of the invention; The bushing device is formed by more than gia one bushing section divided radially. The formation of the bushing device from radially divided bushing section sections is advantageous as we can easily install the bushing device on the shaft device. on the side of the invention; The bushing device significantly encircles the shaft device. Shaping the bushing device so that it largely encircles the shaft device is beneficial as it is possible to form a larger contact area between the shaft friction surfaces and the bushing friction surfaces. on the side of the invention; The friction surfaces of the bushing largely encircle the friction surfaces of the shaft. Shaping the friction surfaces of the bushing so that they largely encircle the friction surfaces of the shaft is advantageous as it is possible to form a larger contact area between the friction surfaces of the shaft and the friction surfaces of the bushing. on the side of the invention; The Lila valve] incorporates a rotary sealing device to substantially seal the bushing and valve housing device against joint rotation. Once the axial force of the shaft device reaches a certain level, the friction between the friction surfaces of the bushing and the friction surfaces of the shaft shaft will become very high, so that the means of the bushing rotate with the shaft device, which will greatly reduce the effect of friction of the bushing, and thus increase the risk of overloading one or more parts of the valve. When the fluid control device reaches an extreme position. Therefore, it is advantageous for a valve with a rotary sealing device so that the bushing device is fixed in a rotating manner relative to the old valve. In part of the invention, the rotary sealing device comprises sleeve sealing parts for the sleeve device and valve sealing parts for the valve housing. Thus, a distinctive embodiment of the invention is achieved. on the side of the invention; The bushing sealing parts and the valve sealing parts are interlocking.

It is advantageous to configure the bushing device and the valve housing with interlocking sealing parts so that we can seal the bushing device in an efficient swivel relative to the valve seat. on the side of the invention; The bushing-closing parts protrude from the bushing medium and where the valve-closing shal is formed as one or more indentations in the valve housing. Thus, a distinctive embodiment of the invention is achieved. on the side of the invention; The fluid control device comprises a nut device arranged to engage with a grooved portion of the shaft device. It is advantageous to form the fluid control device with a device nut to mesh with the o>grooved device of the shaft device whereby it is possible dal) the device device with relatively large force 0 by simply turning the device of the shaft. on the side of the invention; The fluid control device comprises a wedge device arranged linearly within the valve housing. Thus, a distinctive embodiment of the invention is achieved. In part of the invention » the intersection area between the friction surface of the first shaft and the friction surface of the second shaft 5 comprises a chamfered or rounded edge. For example; Rotating the tip between two adjacent friction surfaces is beneficial as this makes the tip more durable. on the side of the invention; The friction surface of the first shaft and the friction surface of the second shaft on the shaft medium are axially spaced from each other. The formation of the friction surface of the first drive shaft away from the friction surface of the second drive shaft on the shaft device - so that the friction surface of the first and second drive shaft does not contiguous - is beneficial as it is possible to design a more useful drive shaft device under certain circumstances. on the side of the invention; The first bushing friction surface and the second bushing friction surface are axially spaced apart from each other on the shaft medium. Forming the first bushing friction surface away from the second bushing friction surface on the shaft device - so that the first and second bushing friction surfaces do not contiguous - is beneficial as this allows

Under certain conditions, the bushing device is better suited to the valve housing.

In part of the invention” the bushing device comprises at least two axially divided bushing ring parts.

Dividing the bushing device into a number of axially divided bushing loop parts is advantageous since

This allows a simpler fit of the bushing device onto the shaft device and/or may enable a simpler machining process.

In part of the invention, the set of shaft friction surfaces abuts the set of bushing friction surfaces.

In one aspect of the invention “ia” includes the first bushing ring of at least two parts of the bushing ring that are axially divided on the friction surface of the first bushing and where “gia” includes the second bushing ring of two

0 at least of the parts of the bushing ring that are axially divided on the second bushing friction surface.

Formation of the two friction surfaces of the bushing on separate bushing ring segments is advantageous as this allows a simpler fit of the bushing device onto the shaft device and/or may allow simpler machining.

on the side of the invention; The valve comprises a lubrication arranged to provide lubrication between at least ga of the shaft friction group and the bushing group.

Arranging a lubricant in or on the valve is advantageous so that at least the adjacent surfaces between the shaft friction surfaces and the bushing friction surfaces can be lubricated transversely, thus reducing friction during normal valve operation.

It should be noted that in this context the term '(lubrication means) is understood as any type of gap';

0 or any AT ga suitable for distributing lubrication or any other type of passive or active lubricant suitable for providing lubrication between the shaft friction surfaces and the bushing friction surfaces of a valve.

on the side of the invention; The valve is selected from the group consisting of: Shaft actuated gate valves. ball valves; knife valves; Needle valves and plug valves.

The common characteristic of the above valve types is that they all have a shaft

Through it, the state of the internal fluid control device is controlled by rotating the drive shaft. So if done

— 1 1 — these valves, for example, are too tightly closed; At ile eda one or more of the valve may break or deform due to overload. It is therefore particularly advantageous to use the present invention in relation to one or more of the valve types listed above. on the side of the invention; The Ble valve is a shaft operated gate valve.

In pyloric valves, the wedge travels a long distance to open or close the valve proportionally. Thus in shaft actuated gate valves the shaft must be long and therefore particularly susceptible to axial overload which may more simply deform the long and slender shaft device of this type of valve. It is therefore particularly advantageous to use the present invention in connection with this particular type of valve.

on the side of the invention; The bushing device is shaped integrally with the valve housing. When forming the bushing means it is advantageously fused to the valve housing as this simplifies fabrication; LED assembly and handling. BRIEF EXPLANATION OF THE DRAWINGS An embodiment of the invention shall be described, by way of example, but not limited to, hereunder by reference 5 to the figures in which: ;» as Jadu from f forward 4 [Fig. 3: shows a cross section of the ES through the middle of the portal valve; As seen from the side of Jadu. Figure 4: A cross-section shows two parts of a valve stem »as seen in the perspective diagram. Figure 5: Shows the first embodiment of a shaft device, as seen from J forward 3.

— 2 1 — Figure 6: shows a second embodiment of the shaft device; As we can see from the front; Figure 7: A third embodiment of the shaft device is shown; As we can see from the front; Figure 18 shows a cross-section through the middle of the bushing device; As noted from a front in Fig. 9: shows a cross-section through the middle of a bushing device formed by the two parts of a single bushing ring; As we can see from the front; Figure 10: shows a bushing method formed by two parts of a bushing sector; As we can see in drawing J for my perspective. Detailed description: Figure 1 shows a WS gate valve seen in the perspective drawing and Figure 2 shows a partial cross-section through the middle of portal valve 1; As we can see from the front. The gate valve 1, also known as the flow control valve, is a valve 1 that opens with wedge means 17 outside the Bl path passing through the valve housing 3 of valve 1. Its characteristic is A characteristic of the 1 gate valve is that the sealing surfaces between the wedge device 17 and the wedge device seats are quite flat. Therefore 1 gate valves are often used when the fluid flows in a straight line and minimal restriction is desired. The faces of the 0 wedge device 17 of gate valve 1 are often in the form of at least a Wika wedge; But it may also be parallel. In this embodiment the valve 1 includes a gle (valve 3) in which the fluid control means 2 are arranged to allow or prevent fluid flow through the valve housing 3. In this embodiment the valve housing includes end flanges flanges) 22 5 allow connection of the valve 1 with a tube (not shown) at any end of the valve housing 3. In this embodiment the shaft means 4 are in the form of a stem 4

It extends below the top (gle) of the valve 3. In this embodiment the lower part of the shaft device 4 is provided with an external thread 16 that meshes with the internal thread of the nut means 15. The nut device 15 connects In the form of Lily with the wedge device 17 so that when the shaft device 4 rotates, the nut device 15 and the wedge device 17 will move up and down the shaft device 4 depending on the direction of rotation i.e. the fluid control device 2 is arranged to be displaced along the rotational axis ) 7 of the shaft device 4 in a manner identical to the rotation of the shaft device 4. Thus when the wedge device 17 reaches an extreme position - whether it is fully closed or fully open - the wedge device 17 will be physically retarded to prevent further travel. So if the shaft device does not stop Drive 4 from rotating - upon reaching an extreme position - will generate to rotate a large axial load on the shaft device 4 » the fluid control device 2 or other parts of the valve 2 and if the rotation is not stopped at the time the shaft device 4 stops, the wedge device may deform 7 or other parts or valve 1 may be damaged in some way other as a result of axial load. Thus in this embodiment the shaft means 4 is substantially stabilized against axial displacement by means of the collar means 8 comprising a set of collar friction surfaces 5 9 10 arranged to interlock with a set of collar friction surfaces 5081) drive shaft (friction surfaces) 5; 6 of the drive shaft means. The bushing device 8 is largely held against the axial offset by the radial surfaces of the valve housing 3. In this embodiment the upper end of the shaft device extends outside the valve housing 3 ag provided with a connection arrangement 23 in the form of four flat surfaces forming end 0 The top of the shaft device 4 is square. The linkage arrangement 23 makes it possible to rotate the shaft device 4 manually for example by means of a “lie wrench” handwheel or other means or to rotate it automatically by means of a motor actuator or other means. In the AT embodiment the valve 1 may be a globe valve 1 comprising a means of controlling the fluid 2 including a movable disc type element and a fixed ring seat 5 in the generally spherical body. Ball valves 1 are named for their spherical body shape with two valve housing halves separated by an internal septum. This shall have a hole forming a seat on which a screw can be installed

A movable stopper of the fluid control device 2 to close (or lock) the valve 1. The stopper is also called a disc or cylinder. in ball valves 1; The plug is connected to the shaft device 4 which can be actuated from outside the valve housing 3. In another embodiment the valve 1 may be a knife valve 1 which is essentially the same as the gate valve 1 where the wedge device 17 is shaped like a knife Enables the wedge tool 17 to cut through extremely thick liquids or semi-liquid materials. In another embodiment the valve 1 may be a needle valve 1 which is a type of valve in which the fluid control 2 comprises a small port and a grooved needle-shaped plunger. This type of valve 1 allows precise flow regulation; Although it can generally only do this 0 at relatively low flow rates. or; In another embodiment the valve 1 may be another type of shaft actuated valve. Figure 3 shows a cross-section E> through the middle of portal valve 1 as seen from the side. To prevent the wedge means 17 from rotating with the rotation of the shaft means od the wedge means 17 in this embodiment are arranged to be guided by a guide means 24 extending along either 5 sides of the valve housing 3 Fig. 4 showing a partial cross-section of the valve stem 1 as can be seen in the perspective diagram. In this embodiment the valve housing 3 comprises an upper ein (top part) 25 joined to the bottom part 27 of the valve gle 3 by means of bolts 26. During valve assembly 1 The shaft device 4 and the bushing device 8 in this embodiment are first placed in the lower all 0 27 where after the upper galll 25 is installed so that the radial and specifically the axial position of the bushing device 8 is fixed. However in another embodiment this may The position of the sleeve means 8 relative to the valve housing 3 may be fixed in some other way—for example, by special fitting; by means of screws or bolts; by welding or in some other way—or the sleeve means 8 may be shaped integrally with the valve housing 3. The surface angle of Shaft friction SA and bushing friction surface angle CA are the internal angle specifically common between the first and second shaft friction surfaces 5;6 and the friction surface

The first and second bushings 9 10. In this embodiment, the friction surfaces of the shaft 5 are identical; 6 completely with the friction surfaces of the bushing 9 10 so that both the shaft friction surface Ligh SA and the bushing friction surface angle CA are 0154 with this in another embodiment these angles may be OST for example 158 162 168 or greater Load or smaller, for example 9151 148© 141; or smaller too. Lad should note that when the term "(completely match) is used above it does not explicitly exclude some tolerance or also clearance between opposite surfaces 5 ( 6 < 9 < 10- i.e. dag will Clearly some of the tolerances in production.” Variations will exist due to wear and tear and there may be tolerances or intentional clearances such that opposite surfaces 5; 6 9 10 do not touch substantially during travel between the extreme positions of the control 0 in fluid 2. In this Rendering The FTA (first transition angle) between the spindle 7, the shaft medium 4 and the first shaft friction surface 5 is broadly the same as the STA (second transition angle) between the spindle 7 and the second shaft friction surface 6- As also shown in Figures 6 and 7. Therefore in this embodiment where the angle 5 of the shaft friction plane SA is 154" both the first and second transition digs are FTA STA by 13". With this As shown in relation to Fig. 5, this angle may be varied in another embodiment of the invention.In this embodiment a means of drive shaft 4 is made of stainless steel but in another embodiment it may be made of steel, cast iron, titanium, brass, aluminum or other metal or other metal such as plastic; the wood; Ceramics or other sale or any combination thereof. In this embodiment the bushing device 8 may be made of brass but in another embodiment it may be made of cast iron (sh) titanium; aluminum bronze or other metal or other sale such as plastic; wood; ceramic or other sale or any In another embodiment at least one of the corresponding surfaces 5;6 9 10 may have an amount 5 .of surface treatment eg arranged to increase or decrease friction; to lengthen the jee surfaces 5 ;6 ;9 .to prevent wear; To enable lubrication - eg self-lubrication or some other type This means that

In another embodiment it may include one or more matching surfaces 5; 6 9 10 on a metal-ceramic case; from Bale vehicle; Of plastic bale or other type of surface treatment. or in another embodiment one or more of the surfaces 5 may be hardened; 6; 9 10 or include at least some respiration therapy. 130) When the shaft device 4 is made of stainless steel and the bushing device 8 is made of brass the coefficient of friction between the shaft friction surfaces 5; 6 and the friction surfaces of the bushing 9 0 in this case will be about 0.35. With this in another embodiment - specifically if One each of the shaft device 4 and the bushing device 8 made of a different material - the coefficient of friction may be greater - eg 0.45; 0.6; 0.7 or greater - or smaller - eg 0.3 0.25 0.2 or smaller Lead 10 when angles are Friction surface CA (SA) of 154" and coefficient of friction of 0.35 The ratio between friction surface angles CA (SA) and coefficient of friction between shaft friction surfaces 5 < 6 and bushing friction surfaces 9 10 in this case by 440. With this depending on Friction surface angles «CA (SA type of material; lubrication possible) Temperature and other factors This ratio in another embodiment may be higher - eg 490 ¢ 525 575 or Lad higher - or lower - eg 400; 370 » 5 320; or less Lead Fig. 5 shows a first embodiment of the shaft device 4 as seen from the front.In this embodiment the shaft friction surface angle SA between the shaft friction surface The first shaft 5 and the second shaft friction surface 6 approx. 7 and the second shaft friction surface 6. This means that in this embodiment the first travel angle FTA is about 23" and the second travel angle STA is about 9©. The difference in travel angles STA FTA in this embodiment will necessitate the generation of more friction when valve 1 reaches its closed position then when it reaches its maximum open position. In other embodiments the difference in angles of transition STA FTA may be a difference eg depending on the particular use; special valve type or other factors.

The angle of the flat shaft friction surface SA enables us not to reduce the minimum diameter of the shaft device - that is, as a result of the flat shaft friction surface angle SA the first shaft friction surface 5 and the second shaft friction surface 6 can be made to be relatively wider without Reducing the force of the shaft device 4. Figure 6 shows a second embodiment of the shaft device 4; As we can see from the front. In the embodiment shown in the other figures the friction surfaces of the shaft 5 are formed; 6 as reinforcement in the shaft device 4 and the friction surfaces of the bushing 9 10 of the bushing device 8 are formed as a Cie protrusion for meshing with the matching shaft friction surfaces 5; 6. With this in this embodiment the designs are reversed so that the friction surfaces of the shaft 5 are formed; 6 as a protrusion arranged for engagement with matching reinforcement 0 formed by the friction surfaces of the bushing 9 » 10 of the bushing device 8. in dine embodiments in all shapes; The friction surfaces of the shaft 5 are machined; 6 in combination with the shaft device 4. However in another embodiment the shaft friction surfaces 65 6 may be formed separate from but rigidly connected with the shaft device 4 eg by means of bolts; welding; stickers or other means. Fig. 7 shows a third embodiment of the shaft device 4; As we can see from the front. In the embodiment shown in the other figures the shaft device 4 comprises only one set of shaft friction surfaces 5; 6. In this embodiment the shaft device 4 comprises two sets of friction surfaces of the shaft 5; 6 and in the AT embodiment the shaft device 4 may comprise more sets of shaft friction surfaces 5 6- eg three; (ead el or more dead 0 Fig. 8 shows a cross-section through the middle of the bushing device 8, as seen from the front. In this embodiment the bushing device 8 forms as a single complete rigid ring arranged to completely encircle the shaft device 4. In this case it may The bushing device 8 is advantageously fitted to the shaft friction surfaces 5;6 by shrinkage—although other assembly methods are also available to the skilled in Art.

9 © singular; As we can see from the front. In this embodiment the bushing device 8 is divided into two separate bushing-ring parts, allowing the first bushing friction surface 9 to be mounted separately from the second bushing friction surface 10 on the shaft device 4. Figure 10 shows the bushing device 8 formed by the two bushing-sector parts 11; As we can see in the perspective drawing. In this embodiment the sleeve device 8 is subdivided into two separate bushing section segments 11 arranged to largely encircle the shaft device 4 when fitted to the valve housing 3. In this embodiment the sleeve device 8 (Lilia) is provided with a rotational locking device. locking means) 0 12 in the form of collar locking parts 13 arranged to interlock with corresponding valve locking parts 14 (not shown) of the valve housing 3 to close the sleeve means 8 substantially and sheltered Valve 3 opposite the reciprocal rotation. With this in the AT embodiment the rotary locking device 12 may be formed by forming the bushing device 8 to be oval; square or with another shape arranged to match a similar seat in the valve housing 3 or 5 the rotary seal 12 may have dedicated fittings; Bolts or other means capable of locking the sleeve means 8 and the valve housing 3 against mutual rotation. The above invention is represented with reference to particular examples of valves 1; shaft means 4; 8 bushing and other tools. However, it must be understood that the invention is not limited to the specific examples described above but may be designed and altered in a variety of configurations within the scope of the invention as specified in the claims.

— 1 9 — Menu (Valve) 1. (Fluid control means) 2. 5 (Valve housing) 3. (Shaft means) 4 Shaft means (First shaft friction surface) 5. Second shaft friction surface 6. Second shaft friction surface (Rotational axis of shaft means) 7. 0 (Collar means) 8. Bushing device (First collar friction surface) 9. Second collar friction surface 0. Second collar friction surface

Collar sector parts) dla 3a.4 (Nut means) 5.Threaded part of shaft means 8. (Intersection area between first and second shaft friction surface) (First collar ring part) 9. (Second collar ring part) 0. (Lubrication means) 21 5 (End flange) 2

— 2 0 — (Connection arrangement of shaft means) 3. (Guide means) 4. Top part of valve housing ex .5 (Bolt) Threaded 26 (Bottom part of valve housing) 27 5 (Collar friction surface angle) .CA (Shaft friction surface angle) SA (First transition angle) ) I FTA (Second transition angle) Second transition angle .STA

Claims (2)

Protections 1 valve (1) to control fluid flow; Said valve includes: (ssl) valve housing (3) a fluid control means (2) to control said flow of fluid through the valve housing housing) (3) mentioned where the fluid control device is arranged control means) 5 (2) aforementioned Jala valve housing (3) aforementioned Shaft means (4) includes a group of shaft friction surfaces; Shaft friction surfaces (5) (6) mentioned first shaft friction surface (5) and second shaft friction surface (6) arranged at an angle Cus (SA) (shaft friction surface angle) 0 Said (shaft say) (SA) friction surface angle) is an internal angle between the first shaft friction surface mentioned (first shaft friction surface) (5) and mentioned second shaft friction surface (6); Where the aforementioned fluid control means (2) are arranged to be displaced along the rotational axis 5 (7) for shaft means (4) mentioned according to the rotation of shaft slay means (4) mentioned; and collar means (8) include A set of collar friction surfaces (9; 10); includes a set of collar friction surfaces (9 < 10) mentioned on the first collar friction surface (9) mentioned 0 and a second dus collar friction surface (10) arranged at a mutual collar friction surface angle (CA) collar friction said surface angle) is an internal angle between said first collar friction surface (9) and said Cua «Sal (10) (second collar friction surface) 5 Collar friction surfaces (9<10) mentioned for meshing with a group of friction surfaces Shaft (shaft friction surfaces) (5” 6) mentioned; where said SA (shaft friction surface angle) and said collar friction surface angle (CA) are between 120° and 1709 and where collar means are installed (8) mentioned inside valve housing 5 (3) mentioned. 2. valve (1) of claim 1 where said SA shaft friction surface angle and said CA are substantially the same . 3. Valve (1) of claim 1 or 2 where the said SA shaft friction surface angle 0 and collar friction surface angle (CA (surface angle) mentioned between 145" and 165". 4 valve (1) of claim 1, wherein the coefficient of friction between said shaft friction surfaces (5; 6) and those of Collar friction surfaces (9<10) mentioned between 0.1 and 1. 15 5. Valve (1) according to claim 1, where is the ratio between the said friction surface angles (SA, CA) and the friction coefficient between the shaft friction surfaces ) (5<6) mentioned and collar friction surfaces (9<10) mentioned between 150 2005 (Valve) saa 6. (1) according to claim 1; A first transition (FTA) transition angle 0 between said rotational axis (7) of said shaft means (4) and the friction surface of the first shaft friction surface (5) mentioned with a second transition angle (STA) between said (rotational axis) (7) to shaft means (4) mentioned and the aforementioned second shaft friction surface (6). ) mentioned and the second transitio n angle). (STA) listed between 1" and 10". 8. Valve (1) according to any of the Ail protection elements where the shaft means (4) include more than one set of shaft friction surfaces surfaces) (5 6(. 9. Valve (1) according to claim 1 where said collar means (8) comprise more than one set of collar friction surfaces (9 < 10 ). 0. lish valve (1) of claim 1; Where the aforementioned group of (shaft friction surfaces) slay surfaces) (5 < 6) is made from a primary material, and the mentioned group of collar friction surfaces (9; 10) is made of “dl” material, and where it differs The first mentioned article on the second mentioned article. 1. Valve (1) according to claim 1, where the aforementioned group of shaft friction surfaces (5, 6) are made of stainless steel. 2. Mam (Valve) (1) according to claim 1, wherein the said group of collar friction surfaces (9, 10) are made of brass. 3. Valve (1) according to claim 1 where the aforementioned group of shaft friction surfaces (5; 6) are formed circumferentially on the outer all of the shaft means (4) mentioned. 14. Valve (1) according to claim 1 where the collar friction surfaces 0 (9 < 10) mentioned on the inner gall are formed from the collar means (8) mentioned. 5. Valve (1) of claim 1; Cua Said collar means (8) comprise at least one complete solid ring. 6. Valve (1) of claim 1 whereby said collar means 5 (8) are fitted to said shaft means (4) by contraction. 7. Valve (1) according to claim 1; Cua collar means (8) mentioned by more than one glad gia with one radially divided collar sector parts (11). 8. Valve (1) according to claim 1, where said collar means (8) encircle said shaft means (4) substantially. 19. Valve (1) according to claim 1; Cus the said collar friction surfaces (9 < 10) largely encircle the shaft friction surfaces surfaces) (5<6) mentioned. 0. Valve (1) of claim 1, wherein the aforementioned valve includes rotary locking means (12) for closing the collar means 0 (8) mentioned and the valve housing (3) mentioned are highly anti-rotating. 1. Mm (Valve) (1) according to claim 1, wherein said rotary locking means (12) includes collar locking parts (13) of the sleeve means (collar means) (8) mentioned and valve locking parts (14) for said 5 (valve housing) (3). 2. A valve (1) of claim 21 in which the said collar locking parts (13) and the valve locking parts (14) interlock. 3. Valve (1) according to claim 1, where said collar locking parts (13) deviate from said collar means (8) and where such collar locking parts are formed Closing 0 of the valve (valve locking parts) (14) mentioned as one or more indentations in (valve housing) (3) mentioned. 4. Valve (1) according to claim 1, where the aforementioned fluid control means (2) includes nut means (15) arranged for interlocking with 5 Threaded part (16) of the shaft means (4) mentioned. 5 25. Valve (1) of claim 1 where the fluid control means includes (fluid control means) (2) mentioned on a wedge means (17) arranged to be placed linearly — 5 2 — Jala valve housing (3) mentioned. 6. Valve (1) of claim 1, wherein includes the area of intersection between said first shaft friction surface (5) and the second shaft friction surface (6) said on a bevel or rounded edge. 27 valve (1) of claim 1 where said first shaft friction surface (5) and said first shaft friction surface (5) are axially spaced apart Second shaft friction surface (6) mentioned on shaft means (4) mentioned. 8. Valve (1) according to claim 1, where said first collar friction surface (9) and the second collar friction surface are axially separated from each other (10) mentioned. 9. Valve (1) of claim 1 where said collar means (8) comprise at least two axially divided collar ring parts (19; 20). 30. Valve (1) of claim 1 wherein the first collar ring part (19) of at least two axially divided sleeve ring parts comprises collar ring parts) (19; 20) mentioned on the first collar friction surface (9) mentioned and where the gia includes the second collar part 109 (second collar part) (20) for at least two axially divided collar ring parts 0 (19 < 20) mentioned on said second collar friction surface (10). 1. Valve (1) according to claim 1, where said valve (1) comprises lubrication means (21) of a weil order between at least oa of the said group of shaft friction surfaces (5; 6) and the group of 25 collar friction surfaces (9<10) mentioned. 2. Valve (1) of claim 1 where said valve (1) is selected — 2 6 — of the group consisting of : shaft actuated gate valves « ball valves; Knife valves ¢ Needle valves and plug valves. 3. Valve (1) of claim 1, wherein said valve (1) is a shaft-operated gate valve. 34. 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Ry a ; ra Le : PE EG \ Fal AN 0 etc. 17 “mi b BS : : HERE > hs A A : A M SA : on HE H EE Tee WELLAND Ty B : ER 3 N : ا ا کد ا ا ا ا ا ا ا ee Aa M REN ا bi H ا ا ا ا RK oN 1: 0 T L A AHA et SE | Car follows a a a s SE 3 RR HE EE Eo BOUIN b ma i i - except for H i 0 : still a ha 0 ur Li id ion ah SY A F to L SH Tee RE : : 1 A L A : A A A A : A A A A H 0 MR 1 5 Hi Fd rE ER FI RS H ribs CE 0 YH RACH Lod NLT BRT L L G TEE M 01 fig Sued Authority for Intellectual Property RE .¥ + \ A 0 § 8 Ss o + < M SNE A J > E K J TE I UN BE Ca a a a ww > Ld Ed H Ed - 2 Ld, provided that the annual financial consideration is paid for the patent and that it is not null and void for violating any of the provisions of the patent system, layout designs of integrated circuits, plant varieties and industrial designs, or its implementing regulations. 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